Transmission



O. K. KELLEY Dec. 20, 1960 TRANSMISSION 3 Sheets-Sheet 1 Original FiledDec. l0, 1956 a c-TBOYQMJ A TTU/Q/VEY INVENTOR. UJFP/az /Y/Zf?" Dec. 20,1960 0, K, KELLEY 2,964,976

TRANSMISSION Original; Filed Deo. 10, 1956 3 Sheets-Sheet 2 ff @y g ZWif INVENTOR.

A 7- TORNEY Dec. 20, 1960 o. K. KELLEY 2,964,976

TRANSMISSION Original Filed Deo. lO, 1956 3 Sheets-Sheet 5 /600 /600Z000 2200 2400 Z600 Z600 6i/Q 1 INVENToR.

ATTORNEY Q AJA/30H1; Q

United States Patent lO TRANSMISSION Original application Dec. 10, 1956,Ser. No. 627,485.

Divided and this application Jan. 13, 1958, Ser. No. 708,581

Claims. (Cl. 74-677) This application is a division of my applicationSerial No. 627,485 filed December l0, 1956, and now abandoned.

This invention relates to improvements in hydrodynamic torque transferand/or multiplying devices and associated gearing for driving a poweroutput member at Various speed ratios from a power input member. Theseare particularly, although not exclusively, suited to transmissions formotor vehicles, especially heavy vehicles such as locomotives, and suchas transmission is described herein as one example of a device to whichmy invention may be applied. Also, the invention is suitable for torqueconverters or speed reducers which multiply torque, but some features ofthe invention are applicable to transmissions generally.

It is known that a turbine of a hydrodynamic torque converter canreadily be constructed to provide any practical degree of torquemultiplication on starting, but if the torque multiplication issufficiently high on starting then the torque of the turbine vanishes atan impractically low turbine speed. This provides poor acceleration andmay furnish little or no torque as the device approaches coupling orone-to-one speed ratio. On the other hand, a turbine can be constructedto provide acceptable coupling characteristics if or when the turbinereaches approximate impeller speed, but this is done at a sacrifice ofstarting or stall torque and accelerating torque in the middle ranges ofspeed.

The foregoing considerations have lead to the design and construction ofhydrodynamic torque transfer devices, especially torque convertershaving various arrangements of multiple turbines of varying torquecharacteristics with or without torque multiplying gearing. Many ofthose proposed or constructed operate satisfactorily within inherentlimitations which it has heretofore been impractical to avoid, but theyhave the disadvantage of maintaining inadequate torque multiplicationduring intermediate speed ranges. These have produced vehicles whichhave been sluggish in performance after starting. Such known devicesfrequently have been of low efiiciency requiring high operating costs.

My invention seeks to overcome these and other disadvantages of knownhydrodynamic transmissions and to provide an improved transmission whichchanges torque ratio smoothly and continuously, that is by infinitelysmall increments, without shifting of mechanical torque multiplyingdevices such as gears. It seeks to improve the efficiency of torqueconverters and to provide a hydrodynamic torque converter which has ahigh starting torque ratio, and maintains a higher torque ratio than wasformerly had during acceleration to one-to-one drive. In particular Iwant to provide a rugged and powerful transmission of high torque ratiosuitable for heavy vehicles such as railway switching locomotives.

Any converter turbine has the inherent characteristic of providingdiminishing torque multiplication as the turbine speed increases towardimpeller speed, as long as the turbine is operating alone, by which Imean that 2,964,976 Patented Dec. 20, 19.60

ICC

such a way that as the torque multiplication or torque ratio of oneturbine decreases the torque ratios of downstream turbines increase. Byproviding a sufficient number of such turbines the torque ratio of thetorque converter as a whole decreases toward coupling much more slowlythan heretofore, and stays at practically high values over long periodsof acceleration of the vehicle because while the turbines of the seriesare successively fading out, that is their torque multiplcations aredecreasing toward zero, the downstream turbines are increasing theirtorque ratios. This provides a maneuverable vehicle of high performance.

Preferably, I combine a series of axial fiow turbines with a radialinflow turbine and connection each turbine to an output shaft by amechanical connection having a lower mechanical advantage than thatofthe connection' of the preceding turbine of the series, the last onebeing direct or one-to-one. Preferably also, the connection of the finalor radial inflow turbine is two-way and the connections of all the otherturbines are free-wheeling.

In this way during acceleration of the vehicle each turbinel runs fasterthan the next turbine downstream, and as each turbine, except the last,approaches its terminal speed and its torque consequently vanishes, thatturbine is disconnected from the output shaft, and is free to float orturn idly in the oil stream, neither putting out torque' nor taking upany significant amount. For all practical purposes, except for factorssuch as friction losses each free-wheeling turbine may be considered asremoved from the transmission.

The foregoing and other objects and advantages of the invention will beapparent from the annexed description and from the accompanyingdrawings, in which:

Fig. l shows schematically one-half of a longitudinal section of atransmission embodying one form of the invention;

Fig. 2 is a developed view showing the cross sections of blades on thecylinder determined by the line 22 in Fig. l and showing therelationship of the various rotating parts of the hydrodynamic torqueconverter;

Figs. 3 and 3A collectively constitute one-half of a symmetricallongitudinal section of the actual structure of a transmission embodyingone form of the invention, Fig. 3 fitting on the left of Fig. 3A, and

Fig. 4 is a diagram of speed, torque and efficiency curves of atransmission embodying the invention.

General diagrammatic arrangement Referring to Fig. 1 the transmission ingeneral includes an input shaft 10 at the right of the drawing, whichdrives a torque converter 12 which drives planetary reduction gearing,collectively designated 14, which drives an output shaft 16 which may beconnected through any suitable forward and reverse gear, not shown, tothe drive wheels of a locomotive. The construction and arrangement ofthe torque converter separately, of the planetary gearing separately andof the two in combination with each other are believed to include novelfeatures.

The torque converter includes a pump or impeller I of generally knownform, represented. diagrammatically in Fig. l by a single blade 20,rotated by the input shaft 10, as will be explained, and circulatingworking liquid in a closed toroidal path, represented by the dotted line22. A first turbine T1 represented in Fig. 1 by a single blade 24receives liquid from the impeller and delivers liquid to a secondturbine T2 represented by blade 26 from which the liquid flows to athird turbine T3 represented by blade 28 which delivers the liquid to afourth turbine T4 represented by blade 30, from which the liquidows to afifth or final turbine T5, represented by blade 32. The liquiddischarged by T5 returns to the impeller I through a reaction member orguide wheel R of known form represented by blade 34. The reaction memberis locked against reverse rotation by any suitable form of one-waytorque-establishing device 35 or free wheeler having sprags or rollers36 which run free in the direction indicated by the point 37 but arelocked against reverse rotation by a member 38 fixed to a shaft 40secured against rotation to the frame of the transmission, as will beexplained.

In order to have the shaft 40 grounded or fixed againstl rotation withrespect to the frame of the transmission and yet have the drive for theimpeller come in at the righthand end of the transmission, the drivearrangement shown in Figs. 1 and 3A is preferably used. The ground shaft40 is fixed to a support for shafts 42 having a form similar to anepicyclic or planetary carrier which is fixed to the frame 44 of thetransmission. The input shaft drives a ring gear 46 meshing with anysuitable number of gears 48 (only one of which is shown in Fig. l)journalled on shafts 42 which gears drive a gear 50 similar to a sungear which rotates the impeller through a drive sleeve 52. In this way arotary drive from the input shaft to the impeller passes through thesupport of the stationary shaft 40 and makes convenient the constructionand assembly of the torque converter and its associated gearing.

The first turbine T1 is connected to drive an input ring gear 60 of afirst planetary gear rset which includes planet pinion 62 journalled onan output carrier 64 and meshing with a reaction sun gear 66 connectedto the frame 44 through va' one-way torque-establishing device 67 whichprevents reverse rotation but permits forward .rotation' of fliesengear, as is known.

The second turbine T2 is connected directly fo the carrier 64. Thecarrier 64 also drives through a oneway torque-establishing device 68,an input sun gear 70 of a second planetary gear set which includesplanetary pinion 72 mounted on an output carrier 74 and meshing with thesun gear 70 and with a stationary reaction ring gear 76. Rotation of thecarrier 64 forward rotates the sun gear 70 forward and this rotates thecarrier 74 forward which through a one-way torque-establishing device 78drives the output shaft 16 forward.

The carrier 74 may also be driven by a third plane-- tary gear set, theinput sun gear 80 of which is driven directly by the third turbine T3.This drives planets 82 journalled on the previously mentioned carrier 74land meshing with a stationary reaction ring gear 84. The output shaft16 is also driven by the fourth turbine T4 which drives the input ringgear 86 of a fourth planetary gear set having planet pinions S8journalled on a carrier 90 and meshing with a reaction sun gear 92 whichis held against reverse rotation by a one-way torque-establishing device94 between the sun 92 and the ground shaft 40. The carrier 90 is fixedto the output shaft 16. The out` put shaft 16 is also driven by thefifth turbine T5 which is connected directly to the carrier 9i).

The apparatus as so far described operates as follows:

Assume that the input shaft 10 rotates backward or clockwise, as seenfrom the right of Fig. 1. This rotates the impeller I forward orcounterclockwise. as seen from the right of Fig. l so that the impellerblade 20 moves forward toward the eye of the observer. Oil circulatingin the path 22 simultaneously impresses torque on all tive turbineblades. Initially the load shaft 16 is held stationary bv the vehiclewheels so that none of the turbines can rotate. This condition is knownas'stall. The design `and relationship of the turbine blades is suchthat at stall T has' invpressed upon it the highest positive or forwardtorque fror the liduid circulated by the irnpeller and the rositivetorque on the succeeding turbines of the series'decre's'esprogressively, being' least onT5.

In fact, depending on the design of the turbines the torque at stall onsome of the turbine blades can be negative. Even so T1 drives thecarrier 64 at reduced speed which in turn drives the input sun gear 70at reduced speed, which drives carrier 74 at further reduced speed, thusimpressing a double speed reduction, and a consequent double torquemultiplication, on the output shaft 16. This positively carries all theother turbines forward, due' to their connections to the gearing, andthis occurs even in spite of any negative torque on some of theturbines, because the mechanical advantage of the connection of T1 toshaft 16 is the highest of all the turbine connections. y

As the shaft 16 begins to move, driven mainly by T1, T2 issimultaneously impressing torque on the carrier 64 directly, driving thecarrier 74 and the output shaft 16 through a single speed reduction orsingle torque multiplication through the gearset 70-72--76.Simultaneously T2 is impressing torque on the carrier 74 and on theoutput shaft 16 through the single speed reduction of the planetary gearset -82-84 and is adding its torque as multiplied by the latterplanetary gear set to the torque of the preceding turbines. Also T2 isadding its torque to the output shaft 16 through the multiplication ofthe planetary gear set 8688-92, and turbine T5 is adding its torquedirectly to the output shaft 16 through its constant connection theretothrough carrier 90.

As the locomotive begins to move the turbines begin to turn at differentspeeds as determined by the ratios of the various planetary gear sets.Inherently all of the turbines increase in speed and drive the outputshaft faster as the resistance to motion of the output shaft decreases.T1' turns faster than T2, which turns faster than T13', vwhi'ch'in turnis faster than T4, which in turn is faster than T5. It is known that aseach turbine in creases in speed, its torque inherentlydecreases. As T1approaches its lterminal speed, T2 reaches a point where it drives thecarrier 64 faster than T1 can drive that carrier through the speedreduction of the planetary gear set 60-62-66, and the torque exerted byT2 on the carrier 64 becomes greater than the torque which can beexerted on this carrier at this speed by the turbine T1 through the ringgear 60. At this point the one-way torque-establishing device 67 breaksaway and T1 is disconnected mechanically from the system. The sun gear66 rotates forward and the turbine T1 floats idly in the oil'streamneither absorbing nor delivering any appreciable t'orqu. vThe ring gear60 and the sun gear 66 are rotating at the same speed about the axis ofthe transmission as the carrier 64.

As T2 approaches its terminal speed its torque decreases and eventuallyT3 can drive the carrier 74 through the planetary gear set 80-82-84faster than T2 can drive this carrier 74 through the gear set 70-72-76which has a greater speed reduction than that of the gear set 8082-84.At this point the oneway torque-establishing device or clutch 68 breaksaway and the sun gear 70 rotates forward, the turbine T2 beingdisconnected from the drive and floating idly in the stream of oil.

Now T2 is driving the output shaft 16 through the planetary reductiongear set 80-82-84 and the shaft 16 is also being driven by T4 throughthe planetary reduction gear set -86-88-92 and by the turbine T5directly. As the speed of the output shaft further increases and as T3approaches its terminal speed the turbine T4 drives the carrier 90 andthe output shaft through the reduction gear 86-88-92 faster than theoutput shaft can be driven by the turbine T3 through the reduction gearset 80-82-84 which has a lower speed ratio than thatof the reductiongear 86-88-92. At this point the freewheeler 78 breaks away and theshaft 16 is driven solely by the two turbines T4 and T5, all of theotherfturbne's beine disconnected from the 'drive and floating idly inthe oil stream.

n s T4 approaches its terminal speed and the torque of T4 decreases andthe torque of T5 increases the point is reached at which the turbine T5can drive the carrier 90 and the output shaft 16 faster than the turbineT4 can drive them through the reduction gear set 84-86-92. At this pointthe free-wheeler 94 breaks away allowing the sun gear 92 to rotateforward and the turbine T4 to float idly in the oil stream. T5 is nowdriving the output shaft alone, the torque converter being in effect asingle turbine torque converter which multiplies torque according to thecharacteristics of the turbine blades 32 and provides a graduallydecreasing torque ratio with increasing speed of the output shaft untilthe output shaft :is rotating approximately as fast as the turbineimpeller `I and the condition known as coupling occurs.

Fig. 2 shows diagrammatically the relationship of the 'blades of thetorque converter to one another. This figure is a developed or unrolleddiagram of the cross sections or traces of the blades on a cylindricalsurface representing the ow of oil according to the line 22 in Fig. l.The blades are represented as moving from the top toward the bottom ofthe drawing as shown by the rotation arrow in Fig. 2 and oil isrepresented as flowing from right to left as indicated by the oil flowarrow.

The discharge angle of a blade is the angle formed between two planes,the rst of which is determined by the axis of the tnansmission and aradial line passing through the tail edge of the blade and the second ofwhich is tangent at the tail to the camber surface of the blade. Thecamber surface is that curved surface determined by the axes of allcircular cylinders which can be placed within the blade so that eachcylinder is tangent to both side surfaces of the blade. Angles aremeasured between those portions of the planes extending from theintersections of the planes in the axial direction of oil ow and theangle is considered positive when measured from the radial and axialplane in the direction in which oil tends to move the blade. Thisterminology is explained in greater detail, and is illustrated in myapplication for U.S. Patent S.N. 537,472, led September 29, 1955, thedisclosure of which is incorporated herein by reference.

The torque which a turbine delivers is influenced by the velocity of oilstriking the blades and by the angle in space through which the turbineblade deccts the oil. This angle is inuenced in turn not only by thedifierence between the absolute direction in space of the incident oiland the exit angle of the blade itself, but also by the speed of theblade. The entrance angle of incidence of the blade itself does notimportantly effect the angle through which the oil is turned. Oilstrikes the blade in a direction determined by conditions upstream ofthe blade and this direction is wholly independent of the `shape of theblade. Oil leaves the blade in a direction determined both by the shapeof the blade and the speed of its movement. The entrance angle is chosento reduce shock loss or spatter of the incident oil, and so the incidentangle affects the efliciency of the turbine but not itstorque-multiplying characteristic.

In Fig. 2 line 98 is the trace of the radial and axial plane through thetail of the impeller blade 20; the line 100 is the trace of a planewhich is parallel to the radial and axial planes through the tails ofthe turbine blades .24 to 30; the line 102 is the trace of a planeparallel to `the radial and axial plane through the tail of the T5 blade32. Line 104 is the trace of the plane tangent `at the tail of theimpeller blade 20 to the camber surface of that blade. Similarly, thelines 106, 108, 110, 112 and 114 are the traces of planes tangent at thetails to the camber surfaces of blades 24-32 respectively. From this itis seen that the discharge tangle of the impeller blade 20 is about plus45; that the blade 24 of T1 has a discharge angle of about -49; that theT2 blade 26 has an angle of about 57; and T3 blade 28 about -63; T4blade 30 about 66; and T5 blade 32 about -45.

The blades, both pump and turbine, are shaped as shown in Fig. 2 and asexplained in greater detail in my application S.N. 537,472 referred to.The design and rrangement of the blades in combination with thesuccessively decreasing mechanical advantages of the connections of thevarious turbines to the output shaft assures that on starting T1 willdevelop the highest hydrodynamic torque, and that this will bemultiplied and applied to the output shaft by the connection of lowestspeed ratio, that is of highest torque ratio or mechanical advantage.Also, as the hydrodynamic torque developed by the first turbine isinherently decreasing with increasing turbine speed, the hydrodynamictorque of each of the downstream turbines T2, T2' T4 and T5, asinfluenced by upstream functioning turbines, is increasing. For example,the hydrodynamic torque of T2 increases from its starting value (whichmay be low at stall) to a maximum, which maximum occurs when thefree-wheeler 67 breaks away and T1 idles, the torque of T1 being zero atthis point. speed of the load shaft (and of turbine T2) increases in theknown manner of single turbines, for T2 is now in effect the firstturbine in the hydrodynamic series because T1 has no hydrodynamiceffect. While the torque of T2 is decreasing the hydrodynamic torque ofeach of T3, T4 and T5 is increasing. When T2 reaches its terminal speedits torque becomes zero, the free-wheeler 68 breaks away and the torqueof T3 is at its maximum. Then T3 becomes the first `turbine of thehydrodynamic series and its torque decreases as its speed increases,following the laws of single turbines. Likewise, each successive turbineT4 and T5 develops increasing torque to a maximum which occurs when thepreceding turbine begins to idle, and thereafter develops decreasingtorque. Finally, as the speed of output shaft increases, T1, T2, T3 andT4 have all been disconnected from the output shaft and T5 alone drivesthe load.

The conditions just described are illustrated in Fig. 4. The curvelabelled torque ratio shows the overall torque ratio of the transmissionshown in Fig. 1, plotted against output shaft speed in rotations perminute for a given speed or throttle opening of a driving engine. Thisshows that at stall the sum of the hydrodynamic torque ratios of all theturbines, each multiplied by the torque ratio of its connection to theoutput shaft, is very high, being above 4, and off the scale of thecurve. It may be of the order of 8 or more. As the shaft 16 begins toturn, the torque ratio decreases rapidly until at about 450 rpm. theratio is about 3.4, as indicated on the torque ratio curve by the point100. The break or sharp change of slope at this point of the curveindicates that the freewheeler 67 and the sun gear 66 are runningforward and that the first turbine is disconnected from the drive, asexplained above. Thereafter, as the speed o-f the output shaft increasesthe torque ratio of the transmission as a whole decreases more slowlythan before until at about 750 r.p.rn. the torque ratio is about 2.2 asindicated by the point 102, where the brake in the curve indicates thatthe second turbine T2 is disconnected from the drive. Thereafter as thespeed of the output shaft increases the torque ratio of the transmissionas a whole decreases more slowly than it did between point and point 102until at about 1240 r.p.m. the torque ratio is about 1.4 as indicated atthe point 104, where the break in the curve indicates that the thirdturbine T3 is disconnected from the drive and that only T4 and T5 aredriving the output shaft. Thereafter as the speed of the output shaftincreases the torque ratio of the transmission as a whole decreases evenmore slowly until at about 2000 r.p.m. the torque ratio is theoretically1.0, but actually slightly less, for example .98 due to friction losses.This is indicated by the point 106 on the torque ratio curve at whichpoint the freewheeler 94 has bet Thereafter, the torque of T2 decreasesas they gun -to run forward to disconnect the founth turbine T4 from thedrive. Now T5 alone is driving the output shaft in the condition knownas coupling.

It will be observed that on starting the efficiency curve follows thetypical efiiciency curve of torque converters and that between about 300r.p.m. output shaft speed and 450 r.p.m. the transmission is operatingnear its peak efciency, namely between about 75% and 77% Ias shown bythe efficiency curve between the points 108 and 110. The point 110occurs at the same output shaft speed as the point 100 on the torqueratio curve and indicates that when the first turbine has beendisconnected from the drive the falling efficiency begins to increaseagain. This increase continues until a maximum of about 78% is reachedat about 600 r.p.m., after which the efliciency curve droops in typicalmanner until the point 112 is reached, which is the same time that point102 is reached and is when the second turbine is disconnected from thedrive at about 750 r.p.m. The efficiency is now approximately 75%. Afterthe second turbine is disconnected from the drive the efficiency curveagain rises from point 112 to a maximum of about 78%, which is reachedat about 1000 r.p.m. output shaft speed. The curve thereafter droops tothe point 114 which occurs at about 1240 r.p.m., that is where the thirdturbine is disconnected from the drive. Thereafter with increasingoutput shaft speed the eiciency rises to about 80% at about 1800 r.p.m.,following which the curve droops slightly until the output shaft speedis about 2000 r.p.m. and the fourth turbine is disconnected from thedrive as indicated at the point 116. The transmission is now in couplingcondition and the efficiency curve is substantially flat in theneighborhood of 80%, increasing slightly with increasing speed. Thesuccession of humps in the eiciency curve, namely from 108 to 110,` from110 to 112, from 112 to 114, and from 114 to 116 provide a closeapproach to a substantially fiat efficiency curve varying vfrom about75% at about 300 r.p.m. to about 80% at speeds above 1800 r.p.m. Thisarrangement of turbines thus provides a transmission having asubstantially constant efficiency varying from about 75% to 81% at allspeeds above 300 r.p.m. This is a very desirable condition and one whichhas not heretofore been achieved with hydrodynamic torque converters.

Structure When Fig. 3 is fitted on the left of Fig. 3A these figurescollectively show one example of actual structure of a transmissionembodying the invention diagnammatically illustrated in Fig. 1.

The casing 44 of the transmission includes a cylindrical shell 200, afront ange 202 and a combined front bearing retainer and gear shaftsupport 204. The casing 44 also includes a combined rear fiange andbearing support 206, a planetary gear housing 208, a rear flange 210 anda rear bearing retainer 212. The input shaft 10 is splined to a driveiiange 214 by which the transmission can be connected to any suitableengine, not shown. The drive shaft and drive tiange assembly aresupported for rotation in the casing 44 by any suitable anti-frictionbearings 216 in the bearing retainer 204. The drive `shaft 10 may beformed integral with a liange or drum 218 to which is fastened the ringgear 46 which meshes with any suitable number of gears 58, for examplethtree, which in turn mesh with the input sun gear 50 which drives theimpeller through the drive sleeve 52. The gears 58 are mounted on fixedspindles 220 which form part of the support 204 which corresponds to thesupport 42 in Fig. l. The ground shaft 40 is keyed to the support 204 at222 so that the shaft 40 is rigidly supported by the casing 44. Rotationof the drive flange 214 clockwise rotates the impeller Icounterelockwise, as is known.

The support 204 has passages 224 communicating with a passage 226 in theground shaft 40 and with lubrication passages 228 in spindles 220. Thepassages 224 and 226 form a conduit for conveying charging andlubricating oil into or out of the transmission through an exteriorconnection 230 in the carrier and front bearing retainer 204. Theimpeller is supported for rotation by a pair of spacedfriction bearings232 between the shaft 40 and the drive sleeve 52. As will be explainedmore-fully below the shaft 40 also serves as support for the stator, thefourth turbine T4 and the planetary gear set 86-88--90 and.

for this reason the shaft 40 requires support at its left end which isremote from its keyed connection at 222 to the carrier.

All of the turbines, except the fourth turbine T4, and their outputshafts are supported for rotation by the front flange 202 and/or therear flange 206 of the casing 44 by a series of anti-friction bearings,as will now be explained.

The first turbine T1 is formed as part of a cylindrical shell 240secured to a front fiange 242 and a rear fiange 244, all of whichelements together form a casing or con tainer for the torque converterwhich is kept filled with liquid under pressure as is customary. Asealing flange 246 secured to the front flange 242 maintains sealingcontact with the impeller drive sleeve 52. An anti-friction bearing 248between the sealing flange 246 and the carrier 204 supports the T1assembly for rotation at its front end. The T1 assembly is supported forrotation at its rear end by an anti-friction bearing 250 between therear fiange 206 and a bearing sleeve 252 bolted to the fiange 244. Thering gear 60, by which the turbine T1 is connected to the drive, may bebolted between the bearing sleeve 252 and the rear flange 244. Thecontainer formed by the T1 shell and fianges may be sealed to thecarrier 64 by a sealing flange 252 attached to the ring gear 60, whichflange maintains a lsealing contact with a collar 254 forma ing part ofcarrier 64. The reaction sun gear of the planetary gearset 60--62-66 maybe formed integral with the inner race 256 of the free-wheeler whichcorresponds to the free-wheeler 67 of Fig. l, and which is lockedagainst reverse rotation by rollers or sprags 258 bearing against anouter race formed as part of the casing flange 206.

The carrier 64 which drives the sun gear 70 is formed as part of therotating assembly of the second turbine T2. This assembly includes theturbine T2 formed as part of a cylindrical shell 260 secured to a flange262 in turn secured to a bearing hub 264 which is formed integral with adrive sleeve 266, which is keyed to the outer race 268 of a one-waytorque-establishing device corresponding to the free-wheeler 68 in Fig.l. The outer race 268 drives the sun gear 70 only forward through spragsor rollers 270 which bear against an inner race formed integral with thesun gear 70. This free-wheeler may be of a known construction whichprovides bearing support for the outer race 268 on the inner race. Thecarrier 64 includes a flange 272 formed integral with the previouslydescribed sealing collar 254 which is bolted to the bearing hub 264 andthus attaches the carrier 64 to the T2 assembly. The entire T2 assemblyis supported for rotation by an anti-friction bearing 274 between thebearing hub 264 and a bearing ring or support 276 bolted to the rearflange 244 of the T1 assembly. It will be seen that the bearing 250supports the T1 assembly from the flange 206 of the casing 44 and thatthe T1 assembly in turn supports the T2 assembly. The T2 assembly isalso supported through the bearing formed in the free-wheeler 268-270,the sun gear 70 in turn being supported on the T3 assembly, as will nowbe explained.

The T2 assembly includes the turbine proper T3 formed as part of acylindrical shell 280 which is secured to a flange 282 fastened to adrive shaft 284 which drive shaft is supported for rotation at its frontend by an anti-friction bearing 286 between the drive shaft 284 and thebearing hub 264 of the T2 assembly, and is supported for rotation at itsrear end by an anti-friction bearing 288 which is supported by therearmost planetary gear set and by the output shaft 16.

acca-,ore

The output shaft 16 is supported for rotation at its rear end by one ormore anti-friction bearings 290 in the rear bearing retainer 212 and issupported for rotation at its front end by an anti-friction bearing 292in the front end f the T3 drive shaft 284. This arrangement supports theoutput shaft at its two ends, one end being the direct bearing support290 in the casing itself and the other being the series or stack ofanti-friction bearings 292-286-274-250 leading to the casing. The outputshaft can therefore assist in supporting the rear end of the groundshaft 40 and this is accomplished by the pilot bearing 294.

The carrier 74 of the rear planetary gear sets is supported for rotationby an anti-friction bearing 296 mounted between the casing ange 206 andthe front ange 298 forming part of the carrier. The rear flange 300 ofthe carrier 74 is bolted to a drive sleeve 302 which contains a pair ofone-way torque-establishing devices 304 which together correspond to theone-way torque-establishing device 78 in Fig. 1 through which the firstthree turbines drive the output shaft. The drive sleeve 302 is supportedfor rotation on the output shaft 16 by an antifriction bearing 306. Thebearings 296 and 306 thus support the carrier 74 in the casing 44. Therear flange 300 of the carrier contains the previously-mentionedantifriction bearing 28S which supports the rear end of the T3 driveshaft 284. Thus the drive 284 and the entire T3 assembly are supportedfor rotation jointly by the bearings 286 and 288. It was previouslystated that the sun gear 70 is supported for rotation on the drive shaft284, and this is accomplished by bearing sleeves 310, which thus assistin supporting the T2 assembly. The spindles 312 of the carrier 74,carrying planet gears 72 and 82, are supported between the anges 298 and300 in the usual manner. The fixed ring reaction gears 76 and 84 whichmesh respectively with the planet gears 72 and 82 are secured to thehousing 208 and the casing 44 by any suitable means such as bolts 314.The sun gear 70 previously described meshes with the planet gears 72 andthus drives the carrier 74 whenever the sun gear 70 is driven by T1assembly or T2 assembly. The sun gear 80 by which the T3 assembly drivesthe planet carrier 74 through the planet gear 82 is keyed to the rearend of the T3 drive shaft 284.

The T4 assembly includes the turbine proper T4 mounted on spider 316connected to a hub 318 supported on anti-friction bearings 320 on theground shaft 40. The ring gear 86 is suitably bolted to the hub 318. Theplanet gears 88 which mesh with the ring gear 86 are mounted on thespindles 322 forming part of the carrier 90 which includes the flange324 keyed to the front end of the output shaft 16 and bolted to a ring326 secured to the fifth turbine T5. The reaction sun gear 92 whichmeshes with a planet gear 88 is supported for rotation by bearing sleeve328 on the rear end of the ground shaft 40 and is formed integral withthe outer race 330 of a oneway torque-establishing device correspondingto the oneway torque-establishing device 94 in Fig. 1 and having spragsor rollers 332 which run on the inner race 96 formed at the-rear end ofthe ground shaft 40 to prevent reverse rotation and permit forwardrotation of the sun gear 92 in the usual manner.

The liquid circulated by the pump and leading from the fifth turbine T5to the pump passes through any suitable form of stator, reaction member,or guide wheel R having blades 34. The particular form of the reactionmember constitutes no part of the present invention but it may beconstructed, for example, as disclosed in Ger.- man Patent 949,024issued Sept. '13, 1956, the disclosure of which is incorporated hereinby reference.

TheA stator is supported fOr-'rotation-on the ground shaft 40 by` anysuitable bearing vand--is locked against reve'rse' 'rotation *by `anysuitable one-way torque-establishing device corresponding to the one-waytorque establishing device in Fig. 1.v

l0 It has been mentioned that the turbines are connected to the outputshaft through connections of successively decreasing mechanicaladvantage, the mechanical advantage of T1 being highest and T5 beingdirectly connected to the output shaft. The size of the various gearsthrough which the turbines are connected to the output shaft may be soselected that the torque multiplication or mechanical advantage of theconnection of T1 through the double reduction to the output shaft isapproximately 6.5 to 1. The speed ratio of T2 may be about 4.0 to 1,while the speed ratio of the connection of T3 may be about 2.6 to 1 andthat of T4 of about 1.6 to 1.

It will be understood that both the diagrammatic disclosure in Fig. 1and the structure disclosed in Figs. 3 and 3A are only illustrative andthat other forms of the device may be made without departing from theinvention as defined in the claims. In these, various subcombinationsare claimed broadly. For example, while a series of tive turbines isdisclosed, certain sub-combinations of less than five turbines arebelieved to be novel,l and have been claimed without regard to theremaining turbines. Thus, some of the claims define a series of threeturbines and refer to the last turbine of that series, which for thepurposes of such claims may be the second from the last or third fromlast in the entire series of five in the illustrative embodiment oftheinvention. Also, all turbines of the series receive liquid circulated bythe impeller and each may be regarded as receiving liquid from theimpeller, even if there are other turbines between the impeller and theturbine under consideration. Thus, the fifth turbine T5 is regarded asreceiving liquid from the impeller. Likewise, any turbine which is downstream of any other turbine receives liquid from such other turbine, forexample the fifth turbine T5 may be regarded as receiving liquid fromany one of the first four turbines.

I claim:

1. A transmission comprising in combination a hydrodynamic impeller, anoutput shaft and means for rotating the output shaft at a plurality ofranges of speed ratios with respect to the impeller including twoplanetary gearsets of different speed ratios having a common outputcarrier connected to drive the output shaft, each of the gearsets havingan input gear, a reaction gear, and planet gears mounted on said carrierand meshing with the input and reaction gears, a series of turbineshydrodynamically driven by the impeller, one of the turbines beingadapted to receive liquid fro-m the impeller and to deliver liquidsuccessively to the remaining turbines of the series, a drivingconnection between the last turbine of the series to receive liquid andthe input gear of the gearset having the higher speed ratio, a one-waydriving connection between the next-to-last turbine of the series andthe other input gear, and still another planetary gearset having aninput gear connected to the first-mentioned turbine, a reaction gear,and an output memberrhaving a one-way driving connection with thesecond-mentioned input gear.

2. A transmission comprising in combination a hydrodynamic impeller, anoutput shaft and means for rotating the output shaft at a plurality ofranges of speed ratios with respect to the impeller including twoplanetary gearsets of different speed ratios having a common outputcarrier connected to drive the output shaft, each of the gearsets havingan input gear, areaction gear, and planet gears mounted on said carrierand meshing with the input and reaction gears, a series of turbineshydrodynamically driven by the impeller, one of the turbines beingadapted to receive liquid from the impeller and to deliver liquidsuccessively to the remaining turbines of the series, a drivingconnection between the last turbine o-f the series' to receive liquidand the input gear of the gearset having the higher speedv ratio, aone-way driving connection 'between the next-t-o-last turbine of theseries and the other inputge'an and still another planetary gearsethaving'an inputI gear connected'rto the.

1I inst-.mentioned turbine, 4a rasticerecan and an aufruf carrierconnected to the` next-t last turbine of the series.

3.. A transmission corrlprisitxs in cnmbinatcn -a hydrodynamic impeller,an output shaft vand meansforrrotating the output shaft at a pluralityof ranges of speed ratios with respect to the impeller `including twoplanetary gearsets of different speed ratios having a common outputcarrier connected to drive theoutput shaft, each of the gearsets havingLan input gear, a reaction gear, and planet gears mounted on saidcarrier and meshing with the input and reaction gears, a series ofturbines hydrodynamically driven by the impeller, one of the turbinesbeing adapted to receive liquid vfrom the impeller and lto deliverliquid successively to the remaining turbines o f the series, a drivingconnection between the last turbine of the series to receive liquid andthe input gear o f the gearsethaving the higher speedratio, a one-waydriving connection between the next-to-last turbine of the series andthe other input gear, and still another planetary gearset having aninput gear connected to the firstmentioned turbine, `a forwardlyrotatable Ireaction gear held against reverse rotation, -and an outputcarrier connected to the next-to-last turbine of the series.

4. A transmission comprising in combination a hydrodynamic impeller, anoutput shaft and means for rotating the output shaft at different rangesof speed ratios with respect to the impeller including two planetarygearsets of different yspeed ratios having a common output carrierconnected to Ydrive the output shaft in the forward sense of rotationpnly, leach 4of the gearsets having an input gear, areaction gear andplanet gears mounted on said .carrier and meshing with `the in put landreaction gears, f-a series of turbines adaptedto 4`vreceiveV,successively liquid circulated by the impeller, a--drive connectionbetween one turbine and the input gear of the gear set having the higherspeed ratio, a one-way drive connection between the turbine precedingthe first-mentioned turbine and the other input gear, still anotherplanetary gearset having an input gear connected to the turbine whichrst receives Aliquid from the impeller and having a vforwardly rotatablereaction gear held against reverse rotation and having an output memberprovided with a one-way drive connection with the second-mentionedinput-gear, and a fourth turbine receiving liquid from thefirst-mentioned turbine and khaving a drive connection with the voutputshaft independentof said carrier.

5. `A transmission comprising in combination a hydrodynamic impeller,anoutput=shaftand means for rotating the output lshaftat'different rangesof speedratios With respect to the impeller including two planetarygearsets of different speed ratios having a common -output carrierconnected to drive, the output ,shaft in the forward sense of rotationonly, each Vof the gearsets having ,an input gear, a reaction gear andplanet gearsmountedn said carrier and meshing with the input andreaction gears, a series of turbines adaptedto` receive successivelyliquid circulated by the impeller, a drive connection between oneturbine of the series and the input. gearof the gearset having thehigher speed ratio, a one-way drive connection between the turbinepreceding the first-mentioned turbine and the other inputvgear, stillanother planetary gearset having-,an input gear connected to the turbinewhich rst receives liquid from the impeller and having aforwardlyrotatable reaction gear held against reverse rotation andhaving an output memberprovided with a one-way drive connection with thesecond-mentioned input gear, -`and afourth turbine receiving liquidfromA the iirst-mentionedturbine vand `having a drivelconnection withthe out-pnt sha-ftjvnclependentvof lsaid carrier, `the connectionoffsaidfourth turbineand theoutputrshaft includingfafonrthgplanetary gearsethavinganjnput gear, areaction gearfandgan output carrier ,cgnneeted tothe nutpunshaft.

een .transmission .Qamursnglin,combination,alllylffr vthe output`shaftat`diierent ranges of speedaatios with respect to theimpellererincludingvtwo planetaryv gearsets of different speed ratioshaving a commonoutputicarrier connectedtodrive thefoutput'shaft in theforward 'Seine of rotation only, each'of the gearsets having an inputgear, a reaction gearand planet gears mounted on said carrier andmeshing with the input and reaction gears, a ,Series of turbines adaptedto receive successively liquid circul lated by the impeller, a driveconnection between one turbine of the series and the input gear of the`gearset having the higher speed ratio, a one-way drive connectionbetween the turbine preceding the first-mentioned turbine and the otherinput gear, still another planetary gearset having an input gearconnected to the turbine which rst receives liquid from the impeller andhaving a forwardly rotatable reaction gear held against reverse rotationand having an output member provided with a one-way drive connectionwith the second-mentioned infput gear, a fourth turbine receiving liquidfrom the rstmentioned turbine and having a drive connection with theoutput shaft independent of said carrier, the connection of said fourthturbine and the output shaft including a fourth planetary gearset havingan input gear, a reaction gear and an output carrier connected to theoutput shaft, and a fifth turbine connected to the carrier of the fourthgearset.

7. A transmission comprising in combination a hydro.- dynamic radialoutow impeller, an output Shaft and means for rotating the output shaftat different ranges of speed ratios with respect to the impellerincludingtwo planetary gearsets of different speed ratios havinga common output carrier connected to drive the output .shaft in the forwardsense of rotation only, each ofthe gearsets having an inputgear, areaction gear and planet gears mounted on said carrier and meshing withthe input and reaction gears, a series of axial flow turbines adapted toreceive successively liquid circulated by the impeller, a driveconnection between one turbine of the series and the input gear of thegearset having the higher speed ratio, a one-way drive connectionbetween the turbine preceding the first-mentioned turbine and the otherinput gear, still another planetary gearset having an input gearconnected to the turbine which rst receives liquid from the impeller andhaving a forwardly rotatable reaction gear held against reverse rotationand having an output member provided with-a one-way drive connectionwith the second-mentioned input gear, a fourth turbine receiving liquidfrom the first-mentioned turbine and havinga drive connection withv theoutput shaft independent of said carrier, the connection of said fourthturbine and the output shaft including a vfourth planetary gearsethaving an input gear, a reaction gear and an output carrier connected tothe output shaft, and a radial inflow turbine connected to the carrierof the fourth gearset and adapted to receive liquid from the axial owturbines and to return the liquid to the impeller. Y

8. In a transmission having a hydrodynamic torque transmitting device,the combination of an impeller' for circulating liquid through a seriesof turbines; an output shaft; a first planetary gearset having an inputgear connected to the first turbine of the series and having a forwardlyrotatable reaction gear held against reverse rotation and having aplanetary gear meshing with the input and reaction gears and having anoutput member; a second planetary .gearset including an inputgear'adapted to be driven by the output member of the first gearset andhaving a reaction gear and 4having planet gears mounted on anoutput-carrierand meshing with therinput and reactionggears and having aIone-waydriving connection with the output shaft;,asecond turbinereceiving liquid from the first turbine and,l adapted totdrivetheoulputmember of the rstl gear set;athird planetary gearset havingan inputVgear,connected` toa` V third turbineyreceiuing liquid from-the secondturbineranljlituringgay reactgu geai'f and 'having Aplanet-.gearsr-rnounted'on thecarr of the second gearset and meshingwithjheminputcagndfreac- 13 tion gears; a one-way drive connectionbetween the output member of the first gearset and the input gear of thesecond gearset; a fourth turbine receiving liquid from the thirdturbine; a fourth planetary gearset having a forwardly rotatablereaction gear held against reverse rotation and having an input gearconnected to the fourth turbine and having planet gears mounted on acarrier connected to the output shaft and meshing with the input andreaction gears; and a fifth turbine receiving liquid from the fourthturbine and connected to the output shaft.

9. In a transmission having a hydrodynamic torque transmitting device,the combination of an impeller for circulating liquid through a seriesof turbines; an output shaft; a first planetary gearset having an inputgear connected to the first turbine of the series and having a forwardlyrotatable reaction gear held against reverse rotation and having aplanetary gear meshing with the input and reaction gears and having anoutput member; a second planetary gearset including an input gearadapted to be driven by the output member of the first gearset andhaving a reaction gear and having planet gears mounted on an outputcarrier having a one-way driving connection with the output shaft andmeshing with the input and reaction gears; a second turbine receivingliquid from the first turbine and adapted to drive the output memberofthe first gear set; a third planetary gearset having an input gearconnected to a third turbine receiving liquid from the second turbine,having a reaction gear, and having planet gears mounted on the carrierof the second gear set and meshing with the input and reaction gears;the third gearset having a mechanical advantage less than that of thesecond gearset; a one-way drive connection between the output member ofthe first gearset and the input gear of the second gearset; a fourthturbine receiving liquid from the third turbine; a fourth planetarygearset and having a mechanical advantage less than that of the thirdgearset and having a forwardly rotatable reaction gear held againstreverse rotation and having an input gear connected to the fourthturbine and having planet gears mounted on a carrier connected to theoutput shaft and meshing with the input and reaction gears; and a fifthturbine receiving liquid from the fourth turbine and connected to theoutput shaft.

10. In a transmission having a hydrodynamic torque transmitting device,the combination of an impeller for circulating liquid through a seriesof turbines; an output shaft; a first planetary gearset having an inputgear connected to the first turbine of the series and having a forwardlyrotatable reaction gear held against reverse rotation and having anoutput member and having a planetary gear meshing with the input andreaction gears; a second planetary gearset including an input gearadapted to be driven by the output member of the first gearset andhaving a reaction gear and having planet gears mounted on an outputcarrier having a one-way driving connection with the output shaft andmeshing with the input and reaction gears; a second turbine receivingliquid from the first turbine and adapted to drive the output member ofthe first gear set; a third planetary gearset having an input gearconnected to a third turbine receiving liquid fro-m the second turbinehaving a reaction gear, and having planet gears mounted on the carrierof the second gearset and meshing with the input and reaction gears; thethird gearset having a mechanical advantage less than that of the secondgearset; a one-way drive connection between the output member of thefirst gearset and the input gear of the second gearset; a fourth turbinereceiving liquid from the third turbine; a fourth planetary gearset andhaving a mechanical advantage less than that of the third gear set andhaving a forwardly rotatable reaction gear held against reverse rotationand having an input gear connected to the fourth turbine and havingplanet gears mounted on a carrier connected to the output shaft andmeshing with the input and reaction gears; and a fifth turbine receivingliquid from the fourth turbine and connected to the output shaft, eachturbine having the characteristic of providing torque which decreases asthel speed of the turbine increases when no turbine preceding it in theseries is exerting torque on the output shaft, the rst turbine havingthe characteristic of providing torque which is high at stall anddecreases to a vanishing point, and each successive turbine of theseries having the characteristic of exerting torque on the output shaftwhich increases as the turbine speed increases while any turbinepreceding it in the series is exerting torque and decreases as the speedof the turbine increases when there is no preceding turbine in theseries exerting torque on the output shaft.

References Cited in the file of this patent UNITED STATES PATENTS2,293,358 Pollard Aug. 18, 1942 2,316,390 Biermann Apr. 13, 19432,578,450 Pollard Dec. 1l, 1951 2,795,154 Russell June 1l, 1957 FOREIGNPATENTS 666,092 Great Britain Feb. 6, 1952

